A stiffness valve

Abstract

The present invention discloses a rigid valve comprising a valve body and a valve seat. The valve body comprises a movable iron core, a stationary iron core, and a valve core. A receiving cavity is provided at the center of one end of the stationary iron core near the valve seat. A sealing assembly is connected within the receiving cavity and comprises a permanent magnet ring and a magnetic conductive member mounted on the valve core. The space between the inner wall of the magnetic conductive member and the outer wall of the valve core is filled with magnetic fluid for sealing the valve core. A retainer is connected within the receiving cavity and mounted on the valve core. The retainer is circumferentially provided with multiple radially retractable elastic pins. The free ends of the elastic pins elastically abut against the outer wall of the valve core to eliminate or partially eliminate lateral offset of the valve core during axial movement. This rigid valve ensures that the sealing assembly is not easily worn, has excellent sealing performance, and is energy-efficient and noise-reducing.

Description

Technical Field

[0001] The present application relates to the technical field of automobile air suspension system control valves, and in particular to a stiffness valve. Background Art

[0002] Air suspension is a device that controls the vehicle's suspension height through air pressure. In a car's air suspension system, the air suspension control solenoid valve is an important component. Its main function is to control inflation or deflation according to different road conditions and adjust the air spring stiffness. Therefore, this solenoid valve is also called a stiffness valve.

[0003] The stiffness valve of a related automotive air suspension system comprises a valve body, an electromagnetic drive unit, a valve core, and a valve stem. One end of the valve stem is connected to the electromagnetic drive unit's armature and moves synchronously with the armature. The other end of the valve stem is connected to the valve core. Axial movement of the valve stem drives the valve core toward or away from the valve port of the valve body, thereby closing or opening the valve port. Because the internal air pressure of an automotive air suspension system can generate transient high pressures or pressure fluctuations during vehicle movement, the seals surrounding the valve core must possess sufficient sealing performance to ensure reliable closure and opening of the valve core and maintain the performance of the air suspension system. In the related art, the sealing members used for sealing the valve core of the rigid valve mostly adopt an annular sealing ring made of rubber to seal the valve core. For example, the Chinese patent application of the applicant of this case with publication number CN221838802U and the name of a solenoid valve has an annular mounting groove on the inner wall of the accommodating cavity of the stop iron, and an annular sealing body sealed with the valve core is connected in the mounting groove. The inner wall of the annular sealing body is provided with an annular groove along the circumferential direction, and the annular sealing parts at both end edges of the annular groove form a lip-shaped sealing structure with the valve core.

[0004] The aforementioned rigidity valves suffer from the following drawbacks in actual use: During operation, the valve core reciprocates axially at high speed. Because the annular sealing element that seals the valve core is typically made of rubber, friction between the outer circumferential wall of the valve core and the sealing portion can easily cause wear of the annular sealing element, leading to air pressure leakage and poor sealing effectiveness and stability, thus affecting the performance of the vehicle's air suspension system. Furthermore, the friction between the valve core and the annular sealing element inevitably increases the rigidity valve's energy consumption. Furthermore, when the solenoid coil is energized to close the valve, the valve core experiences a high instantaneous velocity, resulting in a rapid closing speed and, in turn, a loud impact noise. Summary of the Invention

[0005] The technical problem to be solved by the present application is to overcome the defects of the above-mentioned related technologies and provide a rigid valve that makes the sealing component not easy to wear, has good sealing effect, low energy consumption and low noise.

[0006] The technical solution of this application is to provide a rigidity valve having the following structure:

[0007] A valve body and a valve seat, wherein the valve body includes a movable iron core, a stationary iron core, and a valve core connected to the movable iron core for opening or closing the valve seat, and an accommodating cavity for accommodating the valve core is provided at the center of one end of the stationary iron core close to the valve seat;

[0008] A sealing assembly is connected in the accommodating cavity, and the sealing assembly includes a permanent magnet ring and a magnetic conductive member sleeved on the valve core, and a magnetic fluid for sealing the valve core is filled between the inner wall of the magnetic conductive member and the outer wall of the valve core;

[0009] A retainer is connected in the accommodating cavity, the retainer is sleeved on the valve core and abuts against one end of the sealing assembly close to the valve seat, the retainer is circumferentially provided with a plurality of radially retractable elastic pins, and the free ends of the elastic pins elastically abut against the outer wall of the valve core, so as to eliminate or partially eliminate the lateral offset of the valve core during axial movement.

[0010] In some embodiments, there are two magnetic conductive parts, which are respectively against the two ends of the permanent magnet ring; the inner wall of the center hole of each magnetic conductive part is provided with a plurality of spaced pole teeth along the axial direction, and an annular gap is provided between the pole teeth and the outer wall of the valve core, and the magnetic fluid is filled in the annular gap.

[0011] In some embodiments, the sealing assembly further includes a magnetic isolation shell, the magnetic isolation shell is connected to the accommodating cavity, and the permanent magnet ring and the magnetic conductive member are both disposed in the magnetic isolation shell.

[0012] In some embodiments, the retaining frame is provided with a plurality of radially extending guide holes along the circumference, and the elastic pins include a plurality of first elastic pins and a plurality of second elastic pins, the first elastic pins and the second elastic pins are respectively slidably connected in the guide holes, and the first elastic pins and the second elastic pins are alternately distributed along the circumference of the retaining frame; an elastic ring coaxial with the retaining frame is connected to the retaining frame, and the tail end of each first elastic pin is against the elastic ring; a plurality of elastomers corresponding one-to-one to the second elastic pins are connected to the retaining frame, and the elastomers are connected to the tail ends of the second elastic pins; the stiffness coefficient of the elastic ring is greater than the stiffness coefficient of the elastomer.

[0013] In some embodiments, the elastic ring is provided with an escape hole for the tail end of the second elastic pin to pass through, and the free ends of the first elastic pin and the second elastic pin are both configured as spherical heads.

[0014] In some embodiments, a radially recessed annular groove is provided on the inner wall of the accommodating cavity, and annular teeth are formed on both sides of the annular groove; the two ends of the permanent magnet ring are respectively against the magnetic conductive part and the end face of the annular teeth, and an annular gap is provided between the annular teeth and the outer wall of the valve core, and the annular gap is filled with magnetic fluid for sealing the valve core.

[0015] In some embodiments, a first sealing member is connected between the outer wall of the magnetic isolation shell and the inner wall of the accommodating cavity, and a second sealing member is connected between the inner wall of the magnetic isolation shell and the magnetic conductive member.

[0016] In some embodiments, a mounting groove coaxial with the accommodating cavity is provided in the accommodating cavity, the magnetic isolation shell is connected in the mounting groove, and one end of the magnetic isolation shell close to the valve seat is open and connected to a magnetic isolation plate.

[0017] In some embodiments, the end of the valve core close to the moving iron core is connected to a first buffer body protruding outward along the axial direction of the valve core, and a second buffer body is connected to the accommodating cavity. When the valve seat is in an open state, the first buffer body and the second buffer body elastically offset each other.

[0018] In some embodiments, a plurality of notches are provided along the circumferential direction at one end of the first buffer body close to the second buffer body, and the second buffer body is configured in a disc shape.

[0019] In summary, the stiffness valve of the present application has the following advantages over related technologies: the sealing assembly of the stiffness valve includes a permanent magnet ring and a magnetic conductive member. Under the influence of the magnetic field generated by the permanent magnet ring, magnetic fluid gathers between the inner wall of the magnetic conductive member and the outer wall of the valve core, thereby sealing the outer wall of the valve core. The magnetic fluid does not wear out or produce pollutants such as dust and impurities caused by wear during the movement of the valve core, and the friction between the magnetic fluid and the valve core is low. Therefore, the stiffness valve uses magnetic fluid to seal the valve core, and its sealing effect and sealing stability are good, the service life is long, and the energy consumption is low. The arrangement of the retainer compensates for the gap between the sealing assembly and the outer wall of the valve core. Specifically, the elastic pins on the retainer exert a certain elastic force on the valve core in the radial direction of the valve core. This elastic force provides lateral support force on the valve core, compensating for lateral or radial displacement of the valve core during axial movement, effectively preventing lateral deviation or lateral swing of the valve core during high-speed axial movement, thereby making the axial movement of the valve core more stable and effectively preventing abnormal noise caused by valve core vibration. In addition, the permanent magnet ring generates a magnetic field. During the axial movement of the valve core to close the valve seat, the valve core cuts the magnetic lines of force generated by the permanent magnet ring to generate resistance, so that the axial movement of the valve core has a damping effect, thereby reducing the speed at which the valve core closes the valve, reducing the impact force between the valve core and the valve seat, and reducing noise. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1This is a structural diagram of Example 1 of a stiffness valve of the present application.

[0021] Figure 2 This is a schematic diagram of the assembly structure of a first embodiment of a stiffness valve of the present application.

[0022] Figure 3 This is a three-dimensional diagram of the cross-sectional structure of Example 1 of a stiffness valve of the present application.

[0023] Figure 4 This is a cross-sectional view of Example 1 of a stiffness valve of the present application.

[0024] Figure 5 This is a schematic structural diagram of a retainer of a first embodiment of a stiffness valve of the present application.

[0025] Figure 6 It is a cross-sectional schematic diagram of a retainer of a first embodiment of a stiffness valve of the present application.

[0026] Figure 7 This is a three-dimensional diagram of the cross-sectional structure of a retainer of a first embodiment of a stiffness valve of the present application.

[0027] Figure 8 This is a schematic diagram of the assembly structure of a retainer in Example 1 of a stiffness valve of the present application.

[0028] Figure 9 This is a three-dimensional diagram of the cross-sectional structure of Example 2 of a stiffness valve of the present application.

[0029] Figure 10 This is a cross-sectional view of a second embodiment of a stiffness valve of the present application.

[0030] Description of reference numerals:

[0031] 1. Valve body, 100. Housing, 101. Magnetic isolation sleeve, 102. Moving iron core, 103. Valve stem, 104. Return spring, 105. Stationary iron core, 106. Accommodating chamber, 107. Valve core, 108. First buffer body, 109. Second buffer body, 110. Inner hole, 111. Mounting groove, 112. Solenoid coil, 2. Valve seat, 200. First air hole, 201. Second air hole, 3. Electrical socket, 4. Sealing assembly , 400, magnetic isolation shell, 401, magnetic conductive part, 402, permanent magnet ring, 403, pole tooth, 404, magnetic fluid, 405, magnetic isolation plate, 406, annular groove, 407, annular tooth, 408, annular groove, 5, first sealing member, 500, second sealing member, 6, retaining frame, 600, guide hole, 601, first elastic pin, 602, second elastic pin, 603, elastic ring, 604, avoidance hole, 605, elastomer. DETAILED DESCRIPTION

[0032] First, those skilled in the art should understand that these embodiments are merely used to explain the technical principles of the embodiments of the present application and are not intended to limit the scope of protection of the embodiments of the present application. Those skilled in the art may adjust them as needed to suit specific application scenarios.

[0033] In the description of the embodiments of this application, it should be noted that, unless otherwise specified or limited, the terms "connected" and "connection" should be understood in a broad sense. For example, they can refer to fixed connections, detachable connections, or integral connections; they can refer to mechanical connections or electrical connections; they can refer to direct connections or indirect connections through an intermediate medium. Those skilled in the art will understand the specific meanings of the above terms in the embodiments of this application based on the specific circumstances.

[0034] In the embodiments of the present application, unless otherwise expressly specified or limited, a first feature being "above" or "below" a second feature may mean that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediate medium. Furthermore, a first feature being "above," "above," and "above" a second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature. A first feature being "below," "below," and "below" a second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is lower in level than the second feature.

[0035] The present application will be further described in detail below with reference to the accompanying drawings and specific embodiments. Example 1:

[0036] See also Figures 1 to 4As shown, an embodiment of the present application discloses a stiffness valve, which is used for air pressure control of an automobile air suspension system. Its structure includes a valve body 1 and a valve seat 2 connected to the valve body 1. The valve body 1 includes an outer shell 100, a magnetic isolation sleeve 101, an electromagnetic coil 112, a moving iron core 102, a static iron core 105 and a valve core 107 connected to the moving iron core 102 for opening or closing the valve seat 2. The valve seat 2 has a valve cavity and a first air hole 200 arranged at the end of the valve seat 2, a plurality of second air holes 201 arranged circumferentially on the side wall of the valve seat 2, and a valve port arranged in the valve seat 2 and connecting the first air hole 200 and the second air hole 201; the valve core 107 can open or close the valve port by axial movement. Specifically, the magnetic isolation sleeve 101 is cylindrical with one end open and the other end closed. The static iron core 105 is connected to the open end of the magnetic isolation sleeve 101 and at least partially extends into the magnetic isolation sleeve 101. The moving iron core 102 is slidably connected in the magnetic isolation sleeve 101, and a reset spring 104 is provided between the moving iron core 102 and the static iron core 105. The reset spring 104 ensures that the moving iron core 102 always has a tendency to move away from the static iron core 105; the valve body 1 also includes a valve stem 103, the static iron core 105 has an inner hole 110, the valve stem 103 is clearance-fitted in the inner hole 110, and one end of the valve stem 103 is connected to the moving iron core 102, and the other end of the valve stem 103 is connected to the valve core 107.

[0037] In this embodiment, an electrical socket 3 is connected to one end of the valve body 1 away from the valve seat 2, and the electrical socket 3 is electrically connected to the circuit of the electromagnetic coil 112. The electromagnetic coil 112 is connected to the outside of the magnetic isolation sleeve 101. The electromagnetic coil 112 is energized to generate electromagnetic force to drive the moving iron core 102 to move axially. The moving iron core 102 drives the valve core 107 to move through the valve stem 103 to adjust the valve opening.

[0038] The first and second air holes 200 and 201 of the stiffness valve in this embodiment communicate with the air spring chambers of the vehicle's air suspension system. When the air spring needs to be closed to maintain or stabilize air pressure, solenoid coil 112 is energized to drive valve core 107 to close the valve opening. When the air spring pressure drops significantly and needs to be replenished, solenoid coil 112 is de-energized, and valve core 107, under the elastic force of return spring 104, opens the valve opening to replenish air pressure.

[0039] In this embodiment, the first air hole 200 and the second air hole 201 both have air inlet and outlet, such as the first air hole 200 for air inlet and the second air hole 201 for air outlet; or the first air hole 200 for air outlet and the second air hole 201 for air inlet.

[0040] Furthermore, in this embodiment, a concave accommodating cavity 106 is provided at the center of one end of the static iron core 105 close to the valve seat 2 for accommodating the valve core 107; the accommodating cavity 106 is cylindrical, and the valve core 107 is at least partially accommodated in the accommodating cavity 106, that is, when the valve core 107 moves axially, a part of the valve core 107 is always in the accommodating cavity 106.

[0041] In order to improve the sealing performance between the outer circumferential wall of the valve core 107 and the inner wall of the accommodating cavity 106, specifically in this embodiment, see Figure 2 、 Figure 3 and Figure 4 As shown, a sealing component 4 for sealing the valve core 107 is connected to the accommodating cavity 106. Specifically, the sealing component 4 includes a permanent magnet ring 402 and at least one magnetic conductive part 401 mounted on the valve core 107. The permanent magnet ring 402 and the magnetic conductive part 401 are fixedly connected to the accommodating cavity 106 and do not move synchronously with the valve core 107. The magnetic conductive part 401 and the permanent magnet ring 402 are distributed in sequence along the axial direction of the valve core 107, and the inner wall of the center hole of each magnetic conductive part 401 is provided with a plurality of spaced pole teeth 403 along the axial direction. An annular gap is provided between the pole teeth 403 and the outer wall of the valve core 107. The annular gap is filled with magnetic fluid 404. The magnetic fluid 404 seals the valve core 107 under the action of the magnetic field of the permanent magnet ring 402. That is, the sealing component 4 is a seal that uses magnetic fluid sealing, wherein the magnetic conductive component 401 is made of magnetic conductive material, and the permanent magnetic ring 402 is actually a permanent magnet. Under the action of the magnetic field generated by the permanent magnetic ring 402, the magnetic fluid 404 gathers in the annular gap between the pole teeth 403 and the outer wall of the valve core 107 and seals the outer wall of the valve core 107. During the movement of the valve core 107, the magnetic fluid 404 will not wear out and pollutants such as dust and impurities generated by wear will not appear, and the friction between the magnetic fluid 404 and the valve core 107 is relatively small; therefore, the stiffness valve uses the magnetic fluid 404 to seal the valve core 107, and its sealing effect and sealing stability are good, the service life is long, and the energy consumption is low.

[0042] It is understandable that magnetic fluid sealing is a relatively mature technical means in the prior art. Magnetic fluid is a process in which magnetic particles are dispersed in a carrier liquid to form a stable colloid. Under the action of a magnetic field, it can form a solid-like structure that resists a certain pressure differential. When there is no magnetic field, it has the fluidity of a liquid and is not easy to settle. Magnetic fluid sealing is a contactless seal. Magnetic fluid has good adaptability and can adapt to sealing surfaces of different roughnesses, and ensures stable and reliable sealing performance. Its working principle is that the magnetic fluid can form an annular sealing barrier under the action of a magnetic field and remain in the sealing gap, thereby achieving a sealing effect. Magnetic fluid sealing is an existing mature technology and will not be described in detail in this embodiment.

[0043] It is easy to understand that when the electromagnetic coil 112 is energized to generate electromagnetic force to drive the movable iron core 102 to move axially, causing the valve core 107 to close the valve seat 2, the speed of the valve core 107 is relatively high, and when the valve core 107 and the valve port of the valve seat 2 collide, the impact force between the two will generate a large noise. To this end, in this embodiment, due to the magnetic field generated by the permanent magnet ring 402 of the sealing assembly 4, when the valve core 107 moves axially to close the valve seat 2, the valve core 107 cuts the magnetic flux lines generated by the permanent magnet ring 402 to generate resistance, which provides a damping effect on the axial movement of the valve core 107, thereby reducing the speed of the valve core 107 closing the valve, reducing the impact force between the valve core 107 and the valve seat 2, and reducing noise.

[0044] Further in this embodiment, see Figure 3 and Figure 4 As shown, to increase the sealing area between the magnetic fluid 404 and the valve core 107 and improve sealing performance, two magnetic conductive members 401 are provided. The two magnetic conductive members 401 are located on either side of the permanent magnet ring 402 and respectively abut against the ends of the permanent magnet ring 402. Under the influence of the magnetic field of the permanent magnet ring 402, the magnetic fluid 404 is concentrated in the annular gap reserved between the pole teeth 403 and the outer wall of the valve core 107, thereby sealing the outer circumferential wall of the valve core 107.

[0045] In the aforementioned embodiment, an annular groove 408 is circumferentially formed on the inner wall of the central hole of each magnetic conductive member 401, and pole teeth 403 are formed on both sides of the annular groove 408. In other embodiments, the number of annular grooves 408 can be increased based on the thickness of the magnetic conductive member 401, and the number of annular grooves 408 along the axial direction of the magnetic conductive member 401 can be set to two, three, or four, etc.

[0046] Furthermore, in this embodiment, in order to facilitate the installation of the sealing assembly 4 and prevent the permanent magnet ring 402 from leaking magnetic flux, thereby increasing the magnetic field strength generated by the permanent magnet ring 402, the sealing assembly 4 further includes a magnetic isolation shell 400; a mounting groove 111 coaxial with the accommodating cavity 106 is provided in the accommodating cavity 106 of the static iron core 105, and the magnetic isolation shell 400 is connected to the mounting groove 111; for details, see Figure 2 、 Figure 3 and Figure 4 As shown, the magnetic isolation shell 400 is a hollow housing connected to the housing cavity 106 of the static iron core 105. The permanent magnet ring 402 and the magnetic conductive member 401 are both disposed within the magnetic isolation shell 400. Furthermore, the magnetic isolation shell 400 is open at one end near the valve seat 2 and closed at the other end away from the valve seat 2. A magnetic isolation plate 405 is connected to the open end of the magnetic isolation shell 400. During assembly, the magnetic conductive member 401 and the permanent magnet ring 402 are first installed within the magnetic isolation shell 400, followed by the magnetic isolation plate 405. Finally, the valve seat 2 is assembled, confining the magnetic conductive member 401 and the permanent magnet ring 402 within the magnetic isolation shell 400.

[0047] In this embodiment, in order to further improve the sealing performance of the rigidity valve, see Figure 3 and Figure 4 As shown, a first sealing member 5 is connected between the outer wall of the closed end of the magnetic isolation shell 400 and the inner wall of the accommodating chamber 106, and a second sealing member 500 is connected between the inner wall of the magnetic isolation shell 400 and the magnetic conductive member 401. Both the first sealing member 5 and the second sealing member 500 are annular sealing rings made of rubber, which ensure good sealing between the outer wall of the magnetic isolation shell 400 and the inner wall of the mounting groove 111, and between the inner wall of the magnetic isolation shell 400 and the magnetic conductive member 401, thereby preventing gas leakage.

[0048] It is easy to understand that an annular gap is provided between the pole teeth 403 of the magnetic conductive member 401 and the outer wall of the valve core 107 for the magnetic fluid 404 to gather and fill, and the magnetic fluid 404 in the annular gap does not provide effective support to the valve core 107 when sealing the valve core 107; and the valve core 107 will cause lateral displacement or lateral swing of the valve core 107 during high-speed axial movement due to its own vibration, wear and assembly accuracy, thereby generating vibration and abnormal sound, and even causing the valve seat 2 to be loosely closed. For this reason, in this embodiment, the stiffness valve is also provided with a retainer 6 to prevent the valve core 107 from lateral displacement or lateral swing during the axial movement of the valve core 107. Specifically, see Figure 3 、 Figure 4 、 Figure 5 、 Figure 6 、 Figure 7 and Figure 8 As shown, the retainer 6 is provided in a circular shape and is fixedly connected to the mounting groove 111 of the accommodating cavity 106. The retainer 6 and the valve core 107 are arranged coaxially. The retainer 6 is sleeved on the valve core 107 and abuts against one end of the sealing assembly 4 close to the valve seat 2. The retainer 6 is provided with a plurality of radially retractable elastic pins along the circumference, and the free ends of the elastic pins elastically abut against the outer wall of the valve core 107. The retainer 6 is used to eliminate or partially eliminate the lateral offset of the valve core 107 during axial movement. Among them, the lateral offset of the valve core 107 during axial movement is also the lateral or radial swing displacement or swing amplitude of the valve core 107 along the valve core 107 during axial movement; in this embodiment, the elastic pin on the retaining frame 6 applies a certain elastic force to the valve core 107 along the radial direction of the valve core 107, and the elastic force provides a lateral support force to the valve core 107, compensating for the lateral or radial offset displacement of the valve core 107 during the axial movement, and can effectively prevent the lateral offset or lateral swing of the valve core 107 during high-speed axial movement, thereby making the axial movement of the valve core 107 more stable, and can effectively prevent abnormal noise caused by the vibration of the valve core 107.

[0049] Further in this embodiment, see Figure 5 、 Figure 6 、 Figure 7 and Figure 8As shown, the retaining frame 6 is provided with a plurality of radially extending guide holes 600 along the circumferential direction, and the elastic pins include a plurality of first elastic pins 601 and a plurality of second elastic pins 602, the first elastic pins 601 and the second elastic pins 602 are respectively slidably connected in the guide holes 600, and the first elastic pins 601 and the second elastic pins 602 are alternately distributed along the circumference of the retaining frame 6; an elastic ring 603 coaxial with the retaining frame 6 is connected to the retaining frame 6, and the tail end of each first elastic pin 601 is against the elastic ring 603; a plurality of elastic bodies 605 corresponding one-to-one to the second elastic pins 602 are connected to the retaining frame 6, and the elastic body 605 is connected to the tail end of the second elastic pin 602; the stiffness coefficient of the elastic ring 603 is greater than the stiffness coefficient of the elastic body 605. That is, in this embodiment, two groups of elastic pins are provided to radially abut the valve core 107, and the two groups of elastic pins are alternately distributed along the circumference of the retainer 6. Because the spring constant of the elastic ring 603 is greater than the spring constant of the elastic body 605, the force exerted on the valve core 107 by the first elastic pin 601 is greater than the force exerted on the valve core 107 by the second elastic pin 602. This reduces the pressure on the valve core 107 while ensuring that the elastic pins provide effective support for the valve core 107, thereby reducing friction and energy consumption during axial movement of the valve core 107. Furthermore, the different and alternating pressures exerted on the valve core 107 by the first and second elastic pins 601, 602 provide a certain damping effect when the valve core 107 deviates or swings laterally at any angle, thereby reducing the frequency of lateral deviation or swing of the valve core 107 and further improving the smoothness of the valve core 107 during movement.

[0050] For example, see Figure 5 and Figure 8 As shown, an annular cavity is provided in the retaining frame 6, and twelve guide holes 600 are provided on the inner wall of the annular cavity along the circumferential direction, all of which extend radially along the annular cavity. The number of first elastic pins 601 and second elastic pins 602 is equal, both six, and they are arranged in the guide holes 600 for alternating sliding along the circumference of the annular cavity. An elastic ring 603 coaxial with the annular cavity is installed in the annular cavity of the retaining frame 6, and the elastic ring 603 is respectively connected to or abutted against the tail end of each first elastic pin 601, and an avoidance hole 604 is provided on the elastic ring 603 for the tail end of the second elastic pin 602 to pass through, and the tail end of each second elastic pin 602 is coaxially connected to an elastic body 605, and the elastic body 605 is abutted against the inner wall of the annular cavity of the retaining frame 6 for limiting position.

[0051] In the aforementioned embodiment, the elastic ring 603 is made of a metal material, such as a thin-walled annular ring made of spring steel, which has good support performance and elastic force. The elastic body 605 is a cylindrical spring, and the axis of the spring coincides with the axis of the second elastic pin 602. The elastic body 605 applies an axial elastic force to the second elastic pin 602 along the axial direction of the second elastic pin 602. The free ends of the first elastic pin 601 and the second elastic pin 602 are both configured as spherical heads, which elastically abut against the outer circumferential wall of the valve core 107 to reduce friction between the elastic pins and the valve core 107.

[0052] It is easy to understand that when the electromagnetic coil 112 loses power, the elastic member between the moving iron core 102 and the static iron core 105 stores a large elastic force, causing the moving iron core 102 to quickly reset, and the first buffer body 108 connected to the end face of the valve core 107 away from the valve seat 2, which is axially protruding, quickly hits the bottom wall of the accommodating cavity 106 of the static iron core 105; although the first buffer body 108 can reduce the impact force between the valve core 107 and the static iron core 105, due to the fact that the first buffer body 108 itself has a certain hardness, it is still inevitable to make a collision noise when the first buffer body 108 collides with the hard static iron core 105. For this reason, in this embodiment, see Figure 3 and Figure 4 As shown, a second buffer body 109 made of a flexible material is connected to the inner bottom wall of the accommodating cavity 106. When the electromagnetic coil 112 is de-energized and the valve seat 2 is in the open state, the first buffer body 108 and the second buffer body 109 abut against each other. Because the first buffer body 108 and the second buffer body 109 are both made of flexible materials, the collision between the first buffer body 108 and the second buffer body 109 is a soft collision. This can greatly weaken the collision force between the valve core 107 and the static iron core 105, significantly reducing collision noise, achieving a good silencing effect, and improving the user experience during use.

[0053] In this embodiment, both the first and second buffer bodies 108, 109 are made of materials such as rubber or silicone, which provide excellent cushioning and shock absorption. The end of the first buffer body 108 closest to the second buffer body 109 is circumferentially provided with multiple notches, and the second buffer body 109 is disc-shaped. These notches prevent the formation of a vacuum within the first buffer body 108 when the first and second buffer bodies 108 collide, preventing adhesion between the first and second buffer bodies 108, 109. Example 2:

[0054] See also Figure 9 and Figure 10As shown, in this embodiment, the sealing assembly 4 has a single magnetic conductive member 401. A radially recessed annular groove 406 is provided on the inner wall of the accommodating cavity 106 of the static iron core 105, and annular teeth 407 are formed on both sides of the annular groove 406. The two ends of the permanent magnet ring 402 respectively abut against the end faces of the magnetic conductive member 401 and the annular teeth 407. An annular gap is provided between the annular teeth 407 and the outer wall of the valve core 107. The gap is filled with a magnetic fluid 404 for sealing the valve core 107. That is, in this embodiment, the static iron core 105 is made of a magnetic conductive material. The annular groove 406 formed on the inner wall of the accommodating cavity 106 of the static iron core 105 forms annular teeth 407 on both sides of the annular groove 406. The annular teeth 407 also constitute another magnetic conductive member. That is, in this embodiment, the other magnetic conductive member is directly integrated with the static iron core 105. This not only saves space but also makes the product structure more compact.

[0055] In this embodiment, the magnetic isolation housing 400 of the sealing assembly 4 is open at both ends. The end of the magnetic isolation housing 400 proximal to the valve seat 2 is not provided with a magnetic isolation plate. Instead, a retaining bracket 6 directly abuts against the end face of the magnetic isolation housing 400, thereby confining the magnetic conductive member 401 and the permanent magnet ring 402 within the magnetic isolation housing 400. This results in a simple and compact structure. The remaining technical solutions of this embodiment are identical to those of the first embodiment described above and will not be further elaborated in this embodiment.

[0056] In the description of the embodiments of the present application, it should be noted that in the description of the present application, terms such as "inside" and "outside" indicating directions or positional relationships are based on the directions or positional relationships shown in the accompanying drawings. This is only for the convenience of description and does not indicate or imply that the device or component must have a specific orientation, be constructed and operated in a specific orientation. Therefore, it cannot be understood as a limitation on the present application.

[0057] In the description of the present application, the description with reference to the terms "one embodiment", "some embodiments", "in the present embodiment", "specific example", or "some examples" means that the specific features, mechanisms, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present application. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, mechanisms, materials or characteristics described can be combined in a suitable manner in any one or more embodiments or examples. In addition, those skilled in the art can combine and combine different embodiments or examples described in this specification and the features of different embodiments or examples, unless they are contradictory.

[0058] The above description is merely a specific embodiment of the present application, but the scope of protection of the present application is not limited thereto. Any changes or substitutions that can be easily conceived by a person skilled in the art within the technical scope disclosed in the present application should be included in the scope of protection of the present application. Therefore, the scope of protection of the present application should be based on the scope of protection of the claims.

Claims

1. A stiffness valve, characterized in that: include A valve body (1) and a valve seat (2), wherein the valve body (1) comprises a moving iron core (102), a stationary iron core (105), and a valve core (107) connected to the moving iron core (102) for opening or closing the valve seat (2), and an accommodating cavity (106) for accommodating the valve core (107) is provided at the center of one end of the stationary iron core (105) close to the valve seat (2); A sealing assembly (4) is connected in the accommodating cavity (106), and the sealing assembly (4) comprises a permanent magnet ring (402) and a magnetic conductive member (401) sleeved on the valve core (107), wherein a magnetic fluid (404) for sealing the valve core (107) is filled between an inner wall of the magnetic conductive member (401) and an outer wall of the valve core (107); A retainer (6) is connected to the accommodating cavity (106), the retainer (6) is sleeved on the valve core (107) and abuts against one end of the sealing assembly (4) close to the valve seat (2), the retainer (6) is provided with a plurality of radially retractable elastic pins along the circumference, and the free ends of the elastic pins elastically abut against the outer wall of the valve core (107), so as to eliminate or partially eliminate the lateral offset of the valve core (107) during axial movement; The retaining frame (6) is provided with a plurality of radially extending guide holes (600) along the circumferential direction, and the elastic pins include a plurality of first elastic pins (601) and a plurality of second elastic pins (602), the first elastic pins (601) and the second elastic pins (602) are respectively slidably connected in the guide holes (600), and the first elastic pins (601) and the second elastic pins (602) are alternately distributed along the circumferential direction of the retaining frame (6); an elastic ring (603) coaxial with the retaining frame (6) is connected to the retaining frame (6), and the tail end of each first elastic pin (601) is against the elastic ring (603); a plurality of elastic bodies (605) corresponding to the second elastic pins (602) are connected to the retaining frame (6), and the elastic bodies (605) are connected to the tail ends of the second elastic pins (602); the stiffness coefficient of the elastic ring (603) is greater than the stiffness coefficient of the elastic body (605); The elastic ring (603) is provided with a relief hole (604) for the tail end of the second elastic pin (602) to pass through, and the free ends of the first elastic pin (601) and the second elastic pin (602) are both configured as spherical heads.

2. The stiffness valve according to claim 1, characterized in that: There are two magnetic conductive parts (401), and the two magnetic conductive parts (401) are respectively against the two ends of the permanent magnet ring (402); the inner wall of the center hole of each magnetic conductive part (401) is provided with a plurality of spaced pole teeth (403) along the axial direction, and an annular gap is provided between the pole teeth (403) and the outer wall of the valve core (107), and the magnetic fluid (404) is filled in the annular gap.

3. The stiffness valve according to claim 2, characterized in that: The sealing assembly (4) further comprises a magnetic isolation shell (400), wherein the magnetic isolation shell (400) is connected to the accommodating cavity (106), and the permanent magnetic ring (402) and the magnetic conductive member (401) are both arranged in the magnetic isolation shell (400).

4. The stiffness valve according to claim 1, characterized in that: A radially recessed annular groove (406) is provided on the inner wall of the accommodating cavity (106), and annular teeth (407) are formed on both sides of the annular groove (406); the two ends of the permanent magnet ring (402) are respectively against the end faces of the magnetic conductive member (401) and the annular teeth (407), and an annular gap is provided between the annular teeth (407) and the outer wall of the valve core (107), and the annular gap is filled with a magnetic fluid (404) for sealing the valve core (107).

5. The stiffness valve according to claim 3, characterized in that: A first sealing member (5) is connected between the outer wall of the magnetic isolation shell (400) and the inner wall of the accommodating cavity (106), and a second sealing member (500) is connected between the inner wall of the magnetic isolation shell (400) and the magnetic conductive member (401).

6. The stiffness valve according to claim 3, characterized in that: A mounting groove (111) coaxial with the accommodating cavity (106) is provided in the accommodating cavity (106), the magnetic isolation shell (400) is connected in the mounting groove (111), and one end of the magnetic isolation shell (400) close to the valve seat (2) is open and connected to a magnetic isolation plate (405).

7. The stiffness valve according to claim 1, characterized in that: One end of the valve core (107) close to the movable iron core (102) is connected to a first buffer body (108) protruding outward along the axial direction of the valve core (107), and a second buffer body is connected in the accommodating cavity (106). When the valve seat (2) is in an open state, the first buffer body (108) and the second buffer body (109) elastically abut against each other.

8. The stiffness valve according to claim 7, characterized in that: One end of the first buffer body (108) close to the second buffer body (109) is provided with a plurality of notches along the circumferential direction, and the second buffer body (109) is configured in a disc shape.

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